EP0896893A2 - Lastschaltgetriebe für eine fahrbare Arbeitsmaschine - Google Patents
Lastschaltgetriebe für eine fahrbare Arbeitsmaschine Download PDFInfo
- Publication number
- EP0896893A2 EP0896893A2 EP98114490A EP98114490A EP0896893A2 EP 0896893 A2 EP0896893 A2 EP 0896893A2 EP 98114490 A EP98114490 A EP 98114490A EP 98114490 A EP98114490 A EP 98114490A EP 0896893 A2 EP0896893 A2 EP 0896893A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive branch
- branch
- gear
- hydrostatic
- hydrostatic drive
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
- F16H61/47—Automatic regulation in accordance with output requirements for achieving a target output speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/70—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for change-speed gearing in group arrangement, i.e. with separate change-speed gear trains arranged in series, e.g. range or overdrive-type gearing arrangements
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19149—Gearing with fluid drive
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19149—Gearing with fluid drive
- Y10T74/19158—Gearing with fluid drive with one or more controllers for gearing, fluid drive, or clutch
- Y10T74/19163—Gearing with fluid drive with one or more controllers for gearing, fluid drive, or clutch with interrelated controls
Definitions
- the invention relates to a power shift transmission for a mobile Working machine, especially for a vehicle of the country or Construction industry, with one powered by an internal combustion engine Input shaft and an output shaft between which at least one hydrostatic drive branch and at least one mechanical drive branch are provided parallel to each other. It also becomes a method of controlling a power shift transmission for a mobile machine, especially for a vehicle agriculture or construction, in which a part of the Power through one mechanical drive branch and the other Part of the power via a hydraulic motor hydrostatic drive branch on a common output shaft be transmitted.
- a powershift transmission is known, which overall by a coupling provided on the input shaft is controllable.
- the clutch is followed by a planetary gear with which a division of benefits is possible.
- the Planetary gear is a hydrostatic drive branch and a mechanical drive branch connected in parallel, whose two power units via a summing output shaft be brought together.
- an axial piston pump adjustable in the swivel angle is provided, with the two only adjustable jointly in the swivel angle
- Axial piston motors can be controlled to achieve a large ratio to reach.
- the two axial piston motors work on one totalizing output wave.
- This output wave is one Range shaft connected via a mechanical clutch optionally via one of two gear stages with the output shaft is connectable.
- a correspondingly low driving speed takes place Power distribution with the help of the planetary gear, by approx. 75% of the power via the hydrostatic drive branch and about 25% of the power via the mechanical drive branch be transmitted. This affects the relatively low Efficiency in the hydrostatic drive branch is decisive disadvantageous.
- the driving speed is always of the Engine speed dependent, as a direct clutch via the mechanical drive branch is given.
- the axial piston motors are correspondingly high driving speeds swiveled to the swivel angle 0 and thus block the axial piston pump.
- the invention has for its object a powershift transmission to create the type described above, which a high Efficiency - even at low output speeds - having.
- this is the case with a powershift transmission described type achieved in that in the parallel arrangement two separate hydrostatic drive branches are provided are, each having a separate shaft and via synchronizers and gear stages with the output shaft can be coupled, and that both the mechanical drive branch as also the two hydrostatic drive branches, one on the input side have arranged and switchable under load clutch.
- the invention is based on the idea, regardless of whether one or more mechanical ones within the powershift transmission Drive branches are provided, these drive branches on each Case to connect two hydrostatic drive branches in parallel. Every mechanical drive branch and every hydrostatic one On the input side, the drive branch has one switchable under load Coupling on so that there is the possibility of any The point in time while driving and / or working Switch branch on or off.
- the two hydrostatic As a rule drive branches each have several synchronizing devices. Every synchronizer is at least subordinate a gear stage. Under the term “clutch” is a clutch that can be switched under load. Under the The term “synchronization device” is understood to mean a “clutch”, which can only be switched when it is load-free.
- Such a synchronizing device is usually made using synchronizing rings realized that load-free at synchronous speeds can be brought.
- the fact that two hydrostatic Drive branches are provided there is always the possibility Torque via one of the two hydrostatic drives engaged clutch via the synchronization device arranged on it and the downstream gear stage to the Output shaft transmit while the other's clutch hydrostatic branch is disengaged, so that its synchronizers are load-free and thus operated preparatively can be.
- the mechanical drive branch or branches each have a clutch that can be switched under load each at the input of the relevant mechanical drive branch is arranged so that this mechanical drive branch can be turned on or off at any time, which is synonymous with the torque transmission via the mechanical Is drive branch.
- Any mechanical drive branch can - at least for a limited time - together with one of the hydrostatic drive branches are used as is to change a driving and / or working speed required is. If the new driving or working speed has been reached, the torque is advantageously transmitted via the mechanical one Drive branch and a synchronizer one of the two hydrostatic drive branches, its clutch but stays out. There are elements on the hydrostatic Drive branch also for torque transmission via the used mechanical drive branch. It goes without saying that within this range the advantageously high mechanical Efficiency of the mechanical drive branch is used. The Speed of the output shaft, the driving and / or working speed the mobile working machine is determined directly dependent on the speed of the internal combustion engine.
- the new powershift transmission comes with a very small number of individual components such as gears, shafts, couplings, Synchronizers u. Like. In all important Speed ranges there is the possibility of mechanical To use the drive branch alone. In between there is no interruption in tractive power when switching. When a mechanical drive branch for torque transmission alone is used, the power loss is particularly low because the hydrostatic drive branches are also inactive, d. H. not only the relevant clutches are disengaged, but also the hydraulic motors in question are not driven.
- each mechanical Drive branch can at least each a synchronization device of a hydrostatic drive branch and the associated gear stage with the output shaft be detachable. This means that the synchronization devices in question even before engaging the clutch of the respective mechanical drive branch are synchronized and insofar as they do not have to be activated first.
- hydrostatic drive branch results from the dependency the speed of the internal combustion engine with an advantageous high efficiency usable area.
- Each mechanical drive branch only carries one gear wheel with a rotationally fixed with the shaft of the respective hydrostatic Drive branch connected gear forms a gear stage.
- the inventive method of the type described above is characterized in that during significant changes in speed the working machine via the powershift transmission power to be transferred alone over one or two Hydromotors of hydrostatic drive branches on the output shaft is transmitted that while essentially constant Speeds or within predetermined speed ranges the one to be transmitted via the powershift transmission Power transmitted solely via a mechanical drive branch and that the division of power into a mechanical Drive branch and the one or more hydrostatic Drive branches only to initiate or to leave one Power transmission via a mechanical drive branch he follows.
- the hydraulic motors and the couplings of the hydrostatic drive branches are only activated when there are significant changes in speed the machine to be done.
- the hydrostatic In this respect, drive branches are only used for intermediate areas utilized. At constant driving and / or working speeds the torque is 100% mechanical Transfer drive branch. This applies accordingly to one large range depending on the usable speed of the internal combustion engine.
- the hydro motors and the Couplings of the hydrostatic drive branches out of function. Although the pump for the hydraulic medium of the two hydrostatic Drive branches driven by the internal combustion engine. However, since the swivel angle of the pump is set to 0 ° there is negligible power loss.
- the two hydrostatic Drive branches are not necessarily coupled to one another, but can be controlled separately and therefore also differently.
- hydrostatic drive branches For the generation of a constant speed in a mechanical
- the driving speed changes controlled via one or both hydrostatic drive branches.
- Both hydrostatic drive branches can work simultaneously or used together advantageously to the machine to set in motion. When the movement is achieved in general, only one of the two hydrostatic ones is sufficient Drive branches to an intermediate area of torque transmission to drive through.
- Fig. 1 is an internal combustion engine 1 with his Shown wave 2, on the effectiveness of driving and / or Work drive of the mobile working machine takes place.
- the Drive has a mechanical direct drive 3 and two hydrostatic Drive branches 4 and 5.
- the mechanical direct drive 3, a damper 6 can be connected upstream.
- the direct drive 3 and the two hydrostatic drive branches 4 and 5 are arranged in parallel to each other. You can can be used individually or simultaneously.
- These drives 3, 4 and 5 is followed by a gear 7 with an output shaft 8, which is usually used to tap the travel drive.
- the Shaft 2 of the internal combustion engine 1 also forms an input shaft 9 of a powershift transmission 10 with those previously described Details. Downstream from the transmission 7 of the PTO 11 can be provided a further gear 12, for example generate different output speeds and / or Reverse direction of rotation if necessary.
- the powershift transmission 10 with a continuous Provide shaft that starts as an input shaft 9 and as a PTO 11 ends.
- the mechanical one Direct drive 3 housed one axially one behind the other first mechanical drive branch 13 and axially behind it has second mechanical drive branch 14.
- the first mechanical drive branch 13 has a clutch 15, the a coupling half rotatably with the input shaft 9 or one connected therewith through shaft 16 in rotation stands.
- the other coupling half of the coupling 15 is with a Shaft 17 rotatably connected, which is also in a bearing is mounted and on which a gear 18 is rotatably arranged.
- the second mechanical drive branch 14 is constructed accordingly and includes a clutch 19, a shaft 20 and a gear 21.
- the two hydrostatic drive branches 4 and 5 are also over the shaft 2 of the internal combustion engine 1 can be driven. To this end sits on the shaft 2 a gear 22, which with a gear 23 meshes on a pump shaft 24 of a hydraulic pump 25. Of the Hydraulic pump 25 leads a hydraulic line 26 to one Hydraulic motor 27 that leads to the first hydrostatic drive branch 4 heard. A hydraulic line 28 leads accordingly a hydraulic motor 29 of the second hydrostatic drive branch 5. The hydraulic medium is via a return line 30 to the Hydraulic pump 25 returned.
- the hydrostatic drive branch 4 also belongs 27 a coupling 40, one coupling half with a Motor shaft 31 is rotatably connected while the other Coupling half non-rotatably connected to a branch shaft 32 stands.
- a gear 33 is arranged on the branch shaft 32, which is in engagement with the gear 18.
- the synchronizer 34 carries a gear 36 while the synchronizer 35 has a gear 37.
- a gear 38 and a gear 39 are also provided.
- the gears 38 and 39 are connected to one another in a rotationally fixed manner, however, freely rotatably supported on the branch shaft 32.
- the second hydrostatic drive branch 5 is similar built up.
- a motor shaft 41 connected to the hydraulic motor 29 is connected on the output side, carries half of a clutch 42.
- the other half of the clutch 42 sits on a branch shaft 43, which on the other hand carries a gear 44, which with the Gear 21 of the second mechanical drive branch 14 continuously is engaged.
- Also on the branch shaft 43 are in a corresponding Assignment to elements on the branch shaft 32 of the hydrostatic drive branch 4 several synchronizers 45, 46 and 47 are provided, one half of which are each rotatably connected to the branch shaft 43.
- the other half of the synchronizer 45 carries a gear 48, which is in constant engagement with the gear 38. This is illustrated by a dotted arrow line in Fig. 2.
- the Synchronizer 46 has a gear 49, and the Synchronizer 47 carries a gear 50.
- the synchronizers 34, 35, 45, 46 and 47 are on the two hydrostatic drive branches 4 and 5 distributed so that at this embodiment, the hydrostatic drive branch 4 has two synchronizers 34 and 35 during the hydrostatic drive branch 5 three synchronizers owns. The number could also be distributed in reverse or also match.
- gear 51, 52, 53, 54 and 55 are five gears 51, 52, 53, 54 and 55 non-rotatably connected.
- the gear 51 is in constant engagement with the gear 39 of the hydrostatic drive branch 4.
- Gear 52 also meshes with gear 36.
- Gear 54 is in engagement with the gear 37 of the hydrostatic Drive branch 4.
- Connection to the hydrostatic drive branch 5 consists of the gear 53, which is connected to the gear 49 the synchronizer 46 combs. It stands accordingly Gear 55 with the gear 50 of the synchronizer 47 in Connection.
- the hydraulic pump 25 and the two hydraulic motors 27 and 29 are those of the axial piston type with variably controllable Helix angle. Each of the three helix angles can be independent of the other can be set variably.
- the changeable The setting also includes the position 0.
- the couplings 15, 19, 40, 42 are couplings that can be switched under load.
- the synchronizers 34, 35, 45, 46, 47 exist each consisting of two synchronizing rings, which are only switched load-free can be.
- the clutches as well as the synchronizers are designed to engage or disengage, the construction effort of the synchronizing devices is considerable less than the construction effort of the couplings.
- a Coupling 56 can be provided, via which the transmission 12 is engaged becomes.
- the transmission 12 has a first shaft 57, which carries one half of a clutch 58 while the other Half of the clutch 58 has a gear 59.
- the gear 59 is in engagement with a gear 60 of a shaft 61 which still carries a gear 62.
- the gear 62 stands with one Gear 63 on a shaft 64 in connection. On this way can be a relatively slow drive, for. B. for a work tool to be removed.
- To take a comparatively A clutch 65 serves at high speed of shaft 64 with gear 66, which with a gear 67 on the shaft 64 in Intervention stands.
- the embodiment of the powershift transmission 10 according to FIG. 3 corresponds broadly to the embodiment according to FIG. 2, which is why this can be referred to. Only the is missing second mechanical drive branch 14.
- the gear 12 is also somewhat differently here. Since it depends on the training of the Gear 12 does not arrive in detail, however, here an explanation can be omitted, especially since the function anyway can be seen from the drawing. Based on Fig. 3 is also easy to imagine that in mechanical direct drive 3, the mechanical drive branch 14 can also be provided could, the mechanical drive branch 13 is missing.
- the function of the powershift transmission 10 according to FIG. 2 is as follows described in connection with the table of FIG. 5.
- the first column shows different speed levels 1 to 15, like when you start the machine from standstill be run through to a maximum speed can.
- the relevant elements are in assigned columns reproduced, the activation or activation of the element is indicated by an x while a Whitespace refers to a shutdown or inactivation.
- the helix angle of the hydraulic motors 27 and 29 can be adjusted independently. This happens according to speed level 2 below in such a way that at correspondingly high or maximum speed of the internal combustion engine 1 the clutch 40 is opened and deactivated, wherein at the same time the pivot angle of the hydraulic motor 27 is pivoted to 0 becomes.
- the synchronizing device 34 is so far load-free and can now be opened or disengaged, so that in the second gear, the total power over the Transfer hydrostatic drive branch 5 to the output shaft 8 because the synchronizer 45 continues remains active and the performance via the path already described is transmitted.
- the swivel angle of the hydraulic motor 29 changed in such a way that the driving speed at the Output shaft 8 enlarged.
- connection is in connection with the above explanations between the driving speed and the swivel angles the hydraulic pump 25 and the hydraulic motors 27 and 29 can be seen. From this it can also be seen that the swivel angle of the two Hydromotors 27 and 29 independently of one another at different times Way to be adjusted to the speed levels one after the other to go through.
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Abstract
Description
- Fig. 1
- ein schematisches Blockschaltbild mit der Parallelanordnung mindestens eines mechanischen Antriebszweiges in Verbindung mit zwei hydrostatischen Antriebszweigen,
- Fig. 2
- eine Prinzipskizze für die Anordnung der Elemente in den einzelnen Antriebszweigen,
- Fig. 3
- eine ähnliche Prinzipskizze wie Fig. 2, jedoch nur mit einem mechanischen Antriebszweig,
- Fig. 4
- eine prinzipielle Schnittdarstellung durch die Achsen der Antriebszweige und der Ausgangswelle,
- Fig. 5
- eine Tabelle steigender Geschwindigkeitsbereiche für die Ausführungsform des Lastschaltgetriebes gemäß Fig. 2 und
- Fig. 6
- ein Diagramm der Schwenkwinkel der Pumpe und der beiden Hydromotore über der Fahrgeschwindigkeit.
- 1
- - Verbrennungsmotor
- 2
- - Welle
- 3
- - mechanischer Direktantrieb
- 4
- - hydrostatischer Antriebszweig
- 5
- - hydrostatischer Antriebszweig
- 6
- - Dämpfer
- 7
- - Getriebe
- 8
- - Ausgangswelle
- 9
- - Eingangswelle
- 10
- - Lastschaltgetriebe
- 11
- - Zapfwelle
- 12
- - Getriebe
- 13
- - mech. Antriebszweig
- 14
- - mech. Antriebszweig
- 15
- - Kupplung
- 16
- - Welle
- 17
- - Welle
- 18
- - Zahnrad
- 19
- - Kupplung
- 20
- - Welle
- 21
- - Zahnrad
- 22
- - Zahnrad
- 23
- - Zahnrad
- 24
- - Pumpenwelle
- 25
- - Hydropumpe
- 26
- - Leitung
- 27
- - Hydromotor
- 28
- - Leitung
- 29
- - Hydromotor
- 30
- - Rückleitung
- 31
- - Motorwelle
- 32
- - Zweigwelle
- 33
- - Zahnrad
- 34
- - Synchronisiereinrichtung
- 35
- - Synchronisiereinrichtung
- 36
- - Zahnrad
- 37
- - Zahnrad
- 38
- - Zahnrad
- 39
- - Zahnrad
- 40
- - Kupplung
- 41
- - Motorwelle
- 42
- - Kupplung
- 43
- - Zweigwelle
- 44
- - Zahnrad
- 45
- - Synchronisiereinrichtung
- 46
- - Synchronisiereinrichtung
- 47
- - Synchronisiereinrichtung
- 48
- - Zahnrad
- 49
- - Zahnrad
- 50
- - Zahnrad
- 51
- - Zahnrad
- 52
- - Zahnrad
- 53
- - Zahnrad
- 54
- - Zahnrad
- 55
- - Zahnrad
- 56
- - Kupplung
- 57
- - Welle
- 58
- - Kupplung
- 59
- - Zahnrad
- 60
- - Zahnrad
- 61
- - Welle
- 62
- - Zahnrad
- 63
- - Zahnrad
- 64
- - Welle
- 65
- - Kupplung
- 66
- - Zahnrad
- 67
- - Zahnrad
- 68
- - Zahnrad
- 69
- - Umkehrrad
- 70
- - Zahnrad
- 71
- - Kupplung
Claims (10)
- Lastschaltgetriebe (10) für eine fahrbare Arbeitsmaschine, insbesondere für ein Fahrzeug der Land- oder Bauwirtschaft, mit einer von einem Verbrennungsmotor (1) angetriebenen Eingangswelle (9) und einer Ausgangswelle (8), zwischen denen mindestens ein hydrostatischer Antriebszweig (4) und mindestens ein mechanischer Antriebszweig (13) parallel zueinander vorgesehen sind, dadurch gekennzeichnet, daß in der Parallelanordnung zwei separate hydrostatische Antriebszweige (4, 5) vorgesehen sind, die jeweils eine separate Welle (32, 43) aufweisen und über Synchronisiereinrichtungen (34, 35, 45, 46, 47) und Getriebestufen mit der Ausgangswelle (8) kuppelbar sind, und daß sowohl der mechanische Antriebszweig (13) als auch die beiden hydrostatischen Antriebszweige (4, 5) je eine eingangsseitig angeordnete und unter Last schaltbare Kupplung (15, 40, 42) aufweisen.
- Lastschaltgetriebe nach Anspruch 1, dadurch gekennzeichnet, daß in der Parallelanordnung zu den zwei steuerbaren hydrostatischen Antriebszweigen (4, 5) zwei wahlweise nutzbare mechanische Antriebszweige (13, 14) mit je einer vorgeschalteten und unter Last schaltbaren Kupplung (15, 19) vorgesehen sind.
- Lastschaltgetriebe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß jeder mechanische Antriebszweig (13, 14) über mindestens je eine Synchronisiereinrichtung (34, 45) eines hydrostatischen Antriebszweiges (4, 5) und die zugehörige Getriebestufe (18, 33; 21, 44) mit der Ausgangswelle (8) kuppelbar ist.
- Lastschaltgetriebe nach Anspruch 1, dadurch gekennzeichnet, daß jeder hydrostatische Antriebszweig (4, 5) über mehrere Synchronisiereinrichtungen (34, 35; 45, 46, 47) und Getriebestufen (36, 52; 37, 54; 48, 38, 39 51; 49, 53; 50, 55) mit der Ausgangswelle (8) kuppelbar ist.
- Lastschaltgetriebe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß jeder mechanische Antriebszweig (13, 14) nur je ein Zahnrad (18, 21) trägt, das mit einem drehfest mit der Welle (32, 43) des jeweiligen hydrostatischen Antriebszweiges (4, 5) verbundenen Zahnrad (33, 44) eine Getriebestufe (18, 33; 21, 44) bildet.
- Verfahren zum Steuern eines Lastschaltgetriebes (10) für eine fahrbare Arbeitsmaschine, insbesondere für ein Fahrzeug der Land- oder Bauwirtschaft, indem ein Teil der Leistung über einen mechanischen Antriebszweig (13) und der andere Teil der Leistung über einen einen Hydromotor (27) aufweisenden hydrostatischen Antriebszweig (4) auf eine gemeinsame Ausgangswelle (8) übertragen werden, dadurch gekennzeichnet, daß während wesentlicher Geschwindigkeitsänderungen der Arbeitsmaschine die über das Lastschaltgetriebe (10) zu übertragende Leistung allein über einen oder zwei Hydromotore (27, 29) hydrostatischer Antriebszweige (4, 5) auf die Ausgangswelle (8) übertragen wird, daß während im wesentlichen konstanter Geschwindigkeiten oder innerhalb vorgegebener Geschwindigkeitsbereiche die über das Lastschaltgetriebe (10) zu übertragende Leistung allein über einen mechanischen Antriebszweig (13 oder 14) übertragen wird, und daß die Aufteilung der Leistung auf einen mechanischen Antriebszweig (13 oder 14) und den einen oder die mehreren hydrostatische Antriebszweige (4, 5) nur zur Einleitung oder zum Verlassen einer Leistungsübertragung über einen mechanischen Antriebszweig (13 oder 14) erfolgt.
- Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß die beiden Hydromotore (27, 29) der beiden hydrostatischen Antriebszweige (4, 5) mit unterschiedlichen Schwenkwinkeln gesteuert werden, insbesondere mit einem Schwenkwinkel = 0 an einem der Hydromotore.
- Verfahren nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß bei Kupplung eines mechanischen Antriebszweiges (13 oder 14) mit einem hydrostatischen Antriebszweig (4 oder 5) über eine Getriebestufe die Synchronisierung durch Steuerung der Schwenkwinkel der Hydropumpe (25) und des betreffenden Hydromotors (27 oder 29) erfolgt.
- Verfahren nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, daß in den Zeiten, in denen keine Leistung über den betreffenden hydrostatischen Antriebszweig (4, 5) übertragen wird, einerseits der Schwenkwinkel der Hydropumpe (25) auf 0 verstellt wird und andererseits die Kupplung (40, 42) zwischen dem Hydromotor (27, 29) und der mechanischen Getriebestufe des hydrostatischen Antriebszweiges (4, 5) gelöst wird.
- Verfahren nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, daß für die Erzeugung einer konstanten Drehzahl in einem mechanischen Antriebszweig (13 oder 14) die Fahrgeschwindigkeitsänderungen über einen oder beide hydrostatische Antriebszweige (4, 5) ausgesteuert werden.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19734825A DE19734825C1 (de) | 1997-08-12 | 1997-08-12 | Lastschaltgetriebe für eine fahrbare Arbeitsmaschine |
DE19734825 | 1997-08-12 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0896893A2 true EP0896893A2 (de) | 1999-02-17 |
EP0896893A3 EP0896893A3 (de) | 2000-06-07 |
EP0896893B1 EP0896893B1 (de) | 2003-04-23 |
Family
ID=7838685
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98114490A Expired - Lifetime EP0896893B1 (de) | 1997-08-12 | 1998-08-01 | Lastschaltgetriebe für eine fahrbare Arbeitsmaschine |
Country Status (3)
Country | Link |
---|---|
US (1) | US6044728A (de) |
EP (1) | EP0896893B1 (de) |
DE (2) | DE19734825C1 (de) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102008022309A1 (de) | 2008-05-06 | 2009-11-12 | Schaeffler Kg | Schaltwechselgetriebe und Verfahren zu dessen Betrieb |
WO2013017276A1 (de) * | 2011-08-02 | 2013-02-07 | Voith Patent Gmbh | Antriebsstrang für ein kraftfahrzeug, insbesondere schienenfahrzeug |
WO2014122322A1 (en) * | 2013-02-11 | 2014-08-14 | Spicer Off-Highway Belgium N.V. | Hydrostatic and direct drive transmission |
US9989137B2 (en) | 2013-04-12 | 2018-06-05 | Dana Italia S.P.A. | Direct drive hydrostatic transmission |
IT201800002670A1 (it) * | 2018-02-14 | 2019-08-14 | Arbos Group S P A | Trasmissione |
DE102006031279B4 (de) * | 2006-07-06 | 2020-06-04 | Zf Friedrichshafen Ag | Lastschaltbares Getriebe |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2969594B1 (ja) * | 1998-10-02 | 1999-11-02 | 株式会社プロジェット | 補助走行装置付き作業車両 |
DE19954894A1 (de) * | 1999-05-25 | 2000-12-21 | Liebherr Markus | Leistungsverzweigungsgetriebe |
DE10047402A1 (de) * | 2000-09-26 | 2002-04-11 | Deere & Co | Hydrostateinrichtung für ein hydrostatisch-mechanisches Leistungsverzweigungsgetriebe |
DE10123105B4 (de) * | 2001-05-12 | 2010-08-26 | Zf Friedrichshafen Ag | Leistungsverzweigungsgetriebe |
US6904997B2 (en) * | 2001-05-31 | 2005-06-14 | Sauer-Danfoss, Inc. | Compact vehicle transmission |
DE10251939A1 (de) * | 2002-11-08 | 2004-05-19 | Zf Friedrichshafen Ag | Hydrostatischer Radantrieb |
US6872164B2 (en) * | 2002-11-20 | 2005-03-29 | Dana Corporation | Clutch braking in a multi-speed transmission |
GB0329807D0 (en) * | 2003-12-23 | 2004-01-28 | Agco Gmbh & Co | Drive and control method for a vehicle |
DE102004023630A1 (de) * | 2004-05-10 | 2005-12-08 | Zf Friedrichshafen Ag | Antrieb für ein Mobilfahrzeug |
DE102004023631A1 (de) * | 2004-05-10 | 2005-12-08 | Zf Friedrichshafen Ag | Antrieb für Mobilfahrzeuge |
CN100577463C (zh) | 2005-03-10 | 2010-01-06 | Tcm株式会社 | 液压式动力传递装置及作业车辆 |
DE102007038175A1 (de) * | 2007-08-13 | 2009-02-19 | Magna Powertrain Ag & Co Kg | Schaltgetriebe |
GB0910242D0 (en) * | 2009-06-15 | 2009-07-29 | Bamford Excavators Ltd | Hybrid transmission |
DE102013208201B4 (de) * | 2013-05-06 | 2016-03-10 | Zf Friedrichshafen Ag | Lastschaltgetriebe eines Kraftfahrzeugs und Verfahren zur Schaltsteuerung eines Lastschaltgetriebes |
EP3045775B1 (de) * | 2015-01-13 | 2017-05-10 | Oerlikon Graziano S.p.A. | Hydrostatisches antriebssystem für fahrzeuge |
CN104595431B (zh) * | 2015-01-28 | 2019-10-11 | 南京农业大学 | 一种大功率拖拉机液压机械无级变速器 |
CN109737195A (zh) * | 2019-01-24 | 2019-05-10 | 南京农业大学 | 一种hmcvt的嵌套复合式主轴 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0310873A1 (de) * | 1987-10-07 | 1989-04-12 | Xaver Fendt & Co. | Antrieb für ein Nutzfahrzeug |
DE4311084C1 (de) * | 1993-04-03 | 1994-09-22 | Man Nutzfahrzeuge Ag | Antriebseinrichtung eines Fahrzeuges |
DE4402947A1 (de) * | 1994-02-01 | 1995-08-03 | Rexroth Mannesmann Gmbh | Hydrostatisch-mechanischer Antrieb, insbesondere für ein mit einer Brennkraftmaschine ausgestattetes Kraftfahrzeug |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2939342A (en) * | 1958-03-12 | 1960-06-07 | Woydt | Infinitely variable gear |
US3213712A (en) * | 1963-08-08 | 1965-10-26 | Int Harvester Co | Hydromechanical transmission with countershaft gearing |
DE2015945A1 (de) * | 1970-04-03 | 1971-10-21 | Daimler-Benz AG, 7000 Stuttgart-Untertürkheim | Getriebe, insbesondere für Kraftfahrzeuge |
CA1118233A (en) * | 1978-02-16 | 1982-02-16 | Dana Corporation | Hydromechanical transmission |
US4354400A (en) * | 1978-02-16 | 1982-10-19 | Dana Corporation | Hydromechanical transmission |
CA2125415C (en) * | 1993-06-09 | 2000-05-16 | Edward J. Bogema | Twin countershaft transmission and improved power take-off arrangement therefor |
-
1997
- 1997-08-12 DE DE19734825A patent/DE19734825C1/de not_active Expired - Fee Related
-
1998
- 1998-08-01 DE DE59808016T patent/DE59808016D1/de not_active Expired - Lifetime
- 1998-08-01 EP EP98114490A patent/EP0896893B1/de not_active Expired - Lifetime
- 1998-08-11 US US09/132,238 patent/US6044728A/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0310873A1 (de) * | 1987-10-07 | 1989-04-12 | Xaver Fendt & Co. | Antrieb für ein Nutzfahrzeug |
DE4311084C1 (de) * | 1993-04-03 | 1994-09-22 | Man Nutzfahrzeuge Ag | Antriebseinrichtung eines Fahrzeuges |
DE4402947A1 (de) * | 1994-02-01 | 1995-08-03 | Rexroth Mannesmann Gmbh | Hydrostatisch-mechanischer Antrieb, insbesondere für ein mit einer Brennkraftmaschine ausgestattetes Kraftfahrzeug |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006031279B4 (de) * | 2006-07-06 | 2020-06-04 | Zf Friedrichshafen Ag | Lastschaltbares Getriebe |
DE102008022309A1 (de) | 2008-05-06 | 2009-11-12 | Schaeffler Kg | Schaltwechselgetriebe und Verfahren zu dessen Betrieb |
WO2013017276A1 (de) * | 2011-08-02 | 2013-02-07 | Voith Patent Gmbh | Antriebsstrang für ein kraftfahrzeug, insbesondere schienenfahrzeug |
WO2014122322A1 (en) * | 2013-02-11 | 2014-08-14 | Spicer Off-Highway Belgium N.V. | Hydrostatic and direct drive transmission |
US9494222B2 (en) | 2013-02-11 | 2016-11-15 | Dana Italia S.P.A. | Hydrostatic and direct drive transmission |
US9989137B2 (en) | 2013-04-12 | 2018-06-05 | Dana Italia S.P.A. | Direct drive hydrostatic transmission |
IT201800002670A1 (it) * | 2018-02-14 | 2019-08-14 | Arbos Group S P A | Trasmissione |
WO2019159031A1 (en) * | 2018-02-14 | 2019-08-22 | Arbos Group S.P.A. | Transmission |
Also Published As
Publication number | Publication date |
---|---|
US6044728A (en) | 2000-04-04 |
DE19734825C1 (de) | 1999-12-16 |
DE59808016D1 (de) | 2003-05-28 |
EP0896893A3 (de) | 2000-06-07 |
EP0896893B1 (de) | 2003-04-23 |
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